US4046493A - Sliding vane machine - Google Patents

Sliding vane machine Download PDF

Info

Publication number
US4046493A
US4046493A US05/678,495 US67849576A US4046493A US 4046493 A US4046493 A US 4046493A US 67849576 A US67849576 A US 67849576A US 4046493 A US4046493 A US 4046493A
Authority
US
United States
Prior art keywords
pressure
fluid
vanes
space
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/678,495
Other languages
English (en)
Inventor
Torsten Alund
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US4046493A publication Critical patent/US4046493A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3448—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes

Definitions

  • the present invention relates to sliding vane machines comprising in combination a housing, a rotor being rotatable therein, a plurality of axial grooves spaced evenly along the circumference of said rotor, each one of said grooves supporting two vanes, which vanes are axially displaceable in said groove between a first position in which they are entirely contained inside said groove, to a second position in which each separate vane projects axially from the rotor, a number of radially extending partition walls fixed in the housing and dividing the interior thereof into a plurality of pressure chambers, guide means in the housing adapted to bring said vanes to their said first position when a groove during the rotational movement of the rotor passes one and each of said partition walls, a fluid inlet in each one of said pressure chambers, a fluid supply line common for all fluid inlets, a fluid outlet in each one of said pressure chambers, a fluid discharge conduit common for all fluid outlets.
  • Machines of this kind can be used as a motor, whereby the pressure chambers are fed with a pressure fluid, the work of the motor thereby being taken out via the rotor shaft. It is also possible to use the machine as a pump, whereby the rotor shaft is rotated and the rotor is thereby brought to displace the fluid.
  • the invention refers to a control device by means of which an automatic control of the displacement of the sliding vane machine can be obtained and this is achieved by a combination comprising a pressure plate arranged axially displaceable at each axial side of said rotor and in engagement with the ends of the said vanes projecting from the said groove when the vanes are in their said second position, a number of slots arranged in said pressure plates for said partition walls, the axial position of said pressure plates being adjustable following pressure variations in a fluid-containing first space between the pressure plate surface remote from the said vanes and the adjacent end wall of the housing, and a pressure-actuated sliding valve adapted to control the fluid pressure in said space.
  • FIG. 1 shows schematically and in two different sections perpendicularly to the rotor shaft a sliding vane machine of the kind in question.
  • FIG. 2 shows a diametrical section of the sliding vane machine according to FIG. 1,
  • FIG. 3 is an elevation in peripheral direction as seen from the outside of a portion of the internal parts of the machine taken in level with one of the fixed partition walls,
  • FIG. 4 shows a corresponding elevation of a portion taken in level with an axially extending groove in the rotor
  • FIG. 5 shows the control device for the sliding vane machine in one alternative position
  • FIG. 6 shows in a view corresponding to FIG. 5 a further position of the control device.
  • FIG. 1 shows schematically in sections perpendicular to the rotor shaft of the sliding vane machine the design of the machine.
  • This comprises a substantially cylindrical housing 1, which for elucidatory reasons in the figure has been shown in two different sections which are parallel to each other, and where the two different section surfaces have been shown by different cross-hatching.
  • a shaft 2 is rotatably supported in the housing 1 and said shaft having fixed thereto a rotor 3, which, as can be better seen in FIG. 2, has an intermediate portion of substantially the same outer diameter as the inner diameter of the housing, and two comparatively slender end portions located one at each side of the intermediate portion and each having a smaller outer diameter than the inner diameter of the housing.
  • vanes 5 extend radially to the wall of the housing 1 and slide sealingly against this.
  • each pressure chamber is provided with a fluid inlet 7, which communicates with a supply line 8 common for all pressure chambers.
  • Each pressure chamber further has a fluid outlet 9, which outlets all communicate with a common discharge conduit 10.
  • the inlet 7 for each pressure chamber is thereby located at the front end of the pressure chamber as seen in the rotational direction, whereas the outlet 9 is located at the end of the chamber and in such a manner that at least one pair of vanes at all times blocks the inlet 7 from having direct connection with the pertaining outlet 9.
  • FIG. 2 shows in a diametrical section in of FIG. 1 more detailed structure of the sliding vane machine and particularly its control device, which is not shown in FIG. 1.
  • the machine housing 1 is in the example shown built as two substantially circular housing end walls 11, each of which is provided with seats for rolling bearings 12, in which the rotor shaft 2 is supported.
  • the two housing end walls 11 are secured together by means of an annular housing portion 13 with which the end walls form a closed space.
  • the supply line 8 and the discharge conduit 10, are both arranged in the annular housing portion 13.
  • the rotor 3 has an intermediate portion shown with dotted lines 14, which portion extends to the internal wall of the housing portion 13.
  • the axial measure for this rotor portion is somewhat larger than the total axial measure of the radial portions of two vanes and it is substantially equal to the distance between two fixed partition wall portions 6, which are framed in the annular housing portion 13.
  • the vanes 5 which are located in pairs in each one of the axially extending grooves of the rotor, are substantially L-shaped and invertedly L-shaped, respectively.
  • the two web portions of this pair of L-bodies extend radially outwards to sealingly sliding contact against the internal surface of the annular housing portion 13 and the base portions of the L-bodies are arranged in opposite directions.
  • the base portions of the vanes are slidingly fitted in the axially extending grooves of the rotor.
  • the base portion of the vane at its end turned outwards is provided with a sliding shoe 15 against which a spring 16, which is fixed to the rotor exerts an outwardly directed force.
  • a spring 16 which is fixed to the rotor exerts an outwardly directed force.
  • an annular pressure plate 17 At each side of the rotor, between the vane 5 and the end wall 11 of the housing there is arranged an annular pressure plate 17. These pressure plates are secured against rotation relative to the housing and act as sliding surfaces for the vanes.
  • the pressure plates are provided with slots 18 intended for the fixed partition walls 6 and located just in front of them.
  • each pressure plate 17 and the housing end wall 11 adjacent thereto there is a free space 20, which spaces 20 are all in free mutual connection.
  • a control device adapted to exert such a control on the machine that an obedient machine work is obtained in accordance with varying outer loads
  • the control device comprises mainly a sliding valve 23 having a valve body 25, which is displaceable in a valve housing 24, and which valve body is biased in one direction by means of a spring 26.
  • the valve housing has three channels, which communicate with the supply line 8, where a high pressure prevails, with the space 20 between the pressure plate and the housing end wall and with the space 21 with a substantially zero pressure.
  • the valve housing channel from the supply line is branched off to a space where it actuates the valve body 25 in a direction opposite to that of the spring 26.
  • the remote end of the valve body is fitted to one end of an actuating member 27, which can be for instance a bowden cable, which runs via a firmly mounted pulley to second pulley 28, which is connected to one of the pressure plates 17 and from there further to a manually adjustable, actuating means which is not shown. Due to this external adjustment possibility the function of the valve can be modified thereby that the biasing spring force can be altered.
  • the device is shown in its neutral position, i.e. where the rotor shaft works at a steady load, which is set at the manual actuating means. In this position the pressure from the line 8 and the force of the spring 26 balance each other thus that the valve body 25 is at rest in a position where the mutual connections between the three channels of the valve housing are all blocked.
  • FIGS. 3 and 4 show schematic elevations seen from the inner side of the annular housing portion 13 and in towards the rotor shaft and the figures show peripheral parts of the machine as seen in the plane shown in FIG. 2. From FIG. 3 it is seen how a pair of vanes are entirely pushed into a groove in the intermediate portion of the rotor 3 when the fixed partitions are passed and in FIG. 4 it is shown how a pair of vanes 5 engage against the pressure plate 17 in the areas where the vanes are brought out to their working positions.
  • FIG. 5 shows the control device of the sliding vane machine in a position where the load on the rotor shaft increases. Due to the increase in work which hereby must be executed by the fluid in order to rotate the rotor also the pressure in the supply line 8 will increase. Hereby also the pressure which counteracts the biasing force on the valve body 25 will increase and the valve body therefore moves against the action of the spring, until the space 20 is brought in connection with the space 21, which communicates with the ambient atmosphere.
  • FIG. 6 is finally shown the reverse condition in relation to FIG. 5, i.e. the load on the output shaft -- the rotor shaft 2 -- decreases.
  • the load on the output shaft -- the rotor shaft 2 -- decreases.
  • the spring 26 will urge the valve body 25 past its neutral position and to a position in which line 8, which as mentioned before contains fluid under pressure, is connected to space 20 between the pressure plates and the housing end walls 11.
  • the sliding vane machine has the following function.
  • the valve body 25 is displaced thus that the space 20 between the pressure plates 17 and the housing wall 11 will be connected to the space 21 in the interior of the machine which space in principal has zero pressure and communicates with the ambient atmosphere via the opening 22.
  • the pressure fluid which thereby is contained between the pressure plates and the housing walls will be led off through space 21 and the opening 22 and due to the pressure, which acts on the pressure plates, from the pressure oil acting on the vanes, the pressure plates will move outwards against its adjacent housing end wall 11.
  • the active working surface of the vanes will increase whereby the rotational moment in correspondance therewith increases at the same time as the rotational speed in reversed proportion thereto decreases.
  • valve body 25 When the moment on the shaft decreases the valve body 25 will first take up its neutral position where all channels are mutually blocked from each other and thereby preclude contact between anyone of spaces 8, 20 and 21. When the moment on the shaft has been further reduced thus that the oil pressure in the supply line 8 is lower than the pressure from the spring 26 the valve body 25 will be displaced by the spring until its alternative position is reached where the high pressure supply line 8 will be connected to the space 20 between the pressure plates and the housing walls. The pressure plates hereby are urged inwards against each other whereby the vanes 5 are pushed further into the grooves in the intermediate portion of the rotor. Hereby the active working surface of the vanes will be reduced and the rotational moment is decreased at the same time as the speed of the rotor increases. In this way the motor will give a constant output effect no matter of variations in the rotational speed of the rotor.
  • the rotational speed can furthermore be manually influenced by adjustment of the not shown actuating means.
  • the Bowden cable 27 hereby is stretched.
  • the pulley 28 which is attached to the pressure plate 17 will tend to pull the pressure plate in its own direction.
  • the pressure plate will however be retained in its temporary position by means of the pressure fluid in the space 20, whereby the pull of the cable instead will be transferred to the valve body 25, which against action of spring 26 will be pulled to the position in which the space 20 is put in connection with the low pressure space 21, whereby the space 20 is evacuated.
  • the pressure plates will hereby move inwards and the pulley 28 will stretch the cable thus that the valve body 25 is drawn against its neutral position and the movement stops. In this position the machine still can react as earlier described if the fluid pressure increases, i.e. if the working moment of the shaft increases.
  • the rotational speed of the motor and the rotational moment are thus dependent on the position of the manual actuating means and on the fluid pressure.
  • the control valve is modified thus that the connections for the channels from the high pressure space 8 and the low pressure space 21 change place.
  • the cable for the manual actuating means is furthermore drawn in another way as the movement of the pressure plates at an altered pressure will be opposite the movements obtained when the machine works as a motor.
  • the sliding vane machine works as a pump there will be obtained a constant pump pressure thereby that the machine automatically increases or reduces the oil volume pumped in relation to the tendencys of altered pressure.
  • the maximum oil volume pumped is furthermore decided by manual adjustment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US05/678,495 1975-04-21 1976-04-20 Sliding vane machine Expired - Lifetime US4046493A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SW7504554 1975-04-21
SE7504554A SE7504554L (sv) 1975-04-21 1975-04-21 Styranordning vid lamellmaskin

Publications (1)

Publication Number Publication Date
US4046493A true US4046493A (en) 1977-09-06

Family

ID=20324343

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/678,495 Expired - Lifetime US4046493A (en) 1975-04-21 1976-04-20 Sliding vane machine

Country Status (4)

Country Link
US (1) US4046493A (sv)
DE (1) DE2617011A1 (sv)
GB (1) GB1532315A (sv)
SE (1) SE7504554L (sv)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4551080A (en) * 1983-10-19 1985-11-05 Geiger Cletus M Variable displacement sliding vane pump/hydraulic motor
US4561831A (en) * 1980-06-25 1985-12-31 Compagnie De Construction Mecanique Sulzer Rotary hydraulic axially slidable vane device of variable capacity
US5505592A (en) * 1994-03-11 1996-04-09 Zexel Corporation Variable capacity vane compressor
US5660537A (en) * 1995-09-05 1997-08-26 Ford Motor Company Self-regulating fuel supply pump
US6547546B1 (en) * 1998-09-29 2003-04-15 Alexandr Anatolievich Stroganov Rotary machine
US20060213222A1 (en) * 2005-03-28 2006-09-28 Robert Whitesell Compact, modular method and apparatus for liquefying natural gas
US20090087334A1 (en) * 2007-09-28 2009-04-02 Robert Whitesell Sliding Vane Compression and Expansion Device
US20100139613A1 (en) * 2005-03-09 2010-06-10 Pekrul Merton W Plasma-vortex engine and method of operation therefor
US20110116958A1 (en) * 2005-03-09 2011-05-19 Pekrul Merton W Rotary engine expansion chamber apparatus and method of operation therefor
US20110155095A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine flow conduit apparatus and method of operation therefor
US20110158837A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine vane apparatus and method of operation therefor
US8360760B2 (en) 2005-03-09 2013-01-29 Pekrul Merton W Rotary engine vane wing apparatus and method of operation therefor
US8647088B2 (en) 2005-03-09 2014-02-11 Merton W. Pekrul Rotary engine valving apparatus and method of operation therefor
US8689765B2 (en) 2005-03-09 2014-04-08 Merton W. Pekrul Rotary engine vane cap apparatus and method of operation therefor
US8794943B2 (en) 2005-03-09 2014-08-05 Merton W. Pekrul Rotary engine vane conduits apparatus and method of operation therefor
US8800286B2 (en) 2005-03-09 2014-08-12 Merton W. Pekrul Rotary engine exhaust apparatus and method of operation therefor
US8833338B2 (en) 2005-03-09 2014-09-16 Merton W. Pekrul Rotary engine lip-seal apparatus and method of operation therefor
US8955491B2 (en) 2005-03-09 2015-02-17 Merton W. Pekrul Rotary engine vane head method and apparatus
US9057267B2 (en) 2005-03-09 2015-06-16 Merton W. Pekrul Rotary engine swing vane apparatus and method of operation therefor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2502259A1 (fr) * 1981-03-17 1982-09-24 Sulzer Ag Dispositif hydraulique rotatif a stator et rotor et palettes coulissantes, a coulissement axial
DE102015118022B4 (de) 2015-10-22 2024-05-29 Pfeiffer Vacuum Gmbh Rotationsverdrängervakuumpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH122424A (fr) * 1926-10-15 1927-10-01 Annen Robert Machine rotative réversible.
GB657991A (en) * 1949-06-14 1951-10-03 Alan Frank Swain Rotary fluid pump or motor
US3937605A (en) * 1974-02-25 1976-02-10 Karpisek Ladislav Stephan Rotary piston machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH122424A (fr) * 1926-10-15 1927-10-01 Annen Robert Machine rotative réversible.
GB657991A (en) * 1949-06-14 1951-10-03 Alan Frank Swain Rotary fluid pump or motor
US3937605A (en) * 1974-02-25 1976-02-10 Karpisek Ladislav Stephan Rotary piston machine

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4561831A (en) * 1980-06-25 1985-12-31 Compagnie De Construction Mecanique Sulzer Rotary hydraulic axially slidable vane device of variable capacity
US4551080A (en) * 1983-10-19 1985-11-05 Geiger Cletus M Variable displacement sliding vane pump/hydraulic motor
US5505592A (en) * 1994-03-11 1996-04-09 Zexel Corporation Variable capacity vane compressor
US5660537A (en) * 1995-09-05 1997-08-26 Ford Motor Company Self-regulating fuel supply pump
US6547546B1 (en) * 1998-09-29 2003-04-15 Alexandr Anatolievich Stroganov Rotary machine
US8689765B2 (en) 2005-03-09 2014-04-08 Merton W. Pekrul Rotary engine vane cap apparatus and method of operation therefor
US8375720B2 (en) 2005-03-09 2013-02-19 Merton W. Pekrul Plasma-vortex engine and method of operation therefor
US9057267B2 (en) 2005-03-09 2015-06-16 Merton W. Pekrul Rotary engine swing vane apparatus and method of operation therefor
US20100139613A1 (en) * 2005-03-09 2010-06-10 Pekrul Merton W Plasma-vortex engine and method of operation therefor
US20110116958A1 (en) * 2005-03-09 2011-05-19 Pekrul Merton W Rotary engine expansion chamber apparatus and method of operation therefor
US20110155095A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine flow conduit apparatus and method of operation therefor
US20110158837A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine vane apparatus and method of operation therefor
US8360759B2 (en) 2005-03-09 2013-01-29 Pekrul Merton W Rotary engine flow conduit apparatus and method of operation therefor
US8360760B2 (en) 2005-03-09 2013-01-29 Pekrul Merton W Rotary engine vane wing apparatus and method of operation therefor
US8955491B2 (en) 2005-03-09 2015-02-17 Merton W. Pekrul Rotary engine vane head method and apparatus
US8517705B2 (en) 2005-03-09 2013-08-27 Merton W. Pekrul Rotary engine vane apparatus and method of operation therefor
US8523547B2 (en) 2005-03-09 2013-09-03 Merton W. Pekrul Rotary engine expansion chamber apparatus and method of operation therefor
US8647088B2 (en) 2005-03-09 2014-02-11 Merton W. Pekrul Rotary engine valving apparatus and method of operation therefor
US8833338B2 (en) 2005-03-09 2014-09-16 Merton W. Pekrul Rotary engine lip-seal apparatus and method of operation therefor
US8794943B2 (en) 2005-03-09 2014-08-05 Merton W. Pekrul Rotary engine vane conduits apparatus and method of operation therefor
US8800286B2 (en) 2005-03-09 2014-08-12 Merton W. Pekrul Rotary engine exhaust apparatus and method of operation therefor
US20060213222A1 (en) * 2005-03-28 2006-09-28 Robert Whitesell Compact, modular method and apparatus for liquefying natural gas
US7673476B2 (en) * 2005-03-28 2010-03-09 Cambridge Cryogenics Technologies Compact, modular method and apparatus for liquefying natural gas
US20090087334A1 (en) * 2007-09-28 2009-04-02 Robert Whitesell Sliding Vane Compression and Expansion Device

Also Published As

Publication number Publication date
DE2617011A1 (de) 1976-11-04
GB1532315A (en) 1978-11-15
SE388012B (sv) 1976-09-20
SE7504554L (sv) 1976-10-22

Similar Documents

Publication Publication Date Title
US4046493A (en) Sliding vane machine
DE60110832T2 (de) Verstellbare flügelzellenpumpe
US4070132A (en) Variable performance pump
US2255787A (en) Fluid pressure device and system
CA2044326C (en) Scroll type fluid machinery
US5599163A (en) Regenerative pump having movable walls adjacent opposing faces of the impeller
GB2146701A (en) A variable-displacement sliding-vane lubricant pump
US4551080A (en) Variable displacement sliding vane pump/hydraulic motor
US2649739A (en) Constant pressure variable displacement pump
US4046486A (en) Lubrication of fan blade bearings
US3021790A (en) Pump delivery control mechanism
US2969021A (en) Automatic device for adjusting the output of rotary hydraulic machines
US3067689A (en) Variable capacity fluid supply
US3656869A (en) Variable displacement hydraulic pump
US3008423A (en) Variable capacity, reversible flow hydraulic rotary pump and system
US2255781A (en) Rotary fluid pressure device
US3199297A (en) Infinitely variable hydrostatic transmission system
US2696787A (en) Rotary pump
US2552860A (en) Fluid power device
US2775946A (en) Constant delivery variable pressure pump
US3813189A (en) Low fluid fluid motor
US2938469A (en) Pump
US1677996A (en) Hydraulic change-speed gear
US3190074A (en) Hydraulic transmission
US3603698A (en) Axial flow fan wheel